F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids

Abstract

The invention relates to a compressor comprising an axially balanced shaft. A first end 108 of the shaft 100 is disposed in the discharge pressure portion 34 and has a first surface defined by a diameter. F, and a second end 110 of the shaft is placed in the suction pressure portion 36 and has an off-center circular cavity 116 having a second surface defined by a diameter S. The shaft has an axial bore 120 through which the flow pressure can be transmitted between the respective ends of this shaft so that it acts in opposite directions on both flat surfaces of the ends to balance the resulting axial thrust applied to the shaft. </ P> <P> application: fluid compressors, air conditioning, refrigeration systems, etc. </ P>

Description

The invention relates generally to the drive shaft of a

compressor, and in particular

scroll compressors with drive shafts

subject to axial thrust forces.

Usually, a scroll type apparatus, whether used for compression or expansion of a fluid, includes a drive shaft for actuating at least one of the scroll elements in mesh.

Orbital without rotation with the other scroll element.

When the scroll type apparatus is used for compression, the fluid subjected to compression tends to move the end plates supporting the scroll elements away. This spacing is usually counteracted by one or more thrust bearings acting on the orbital scroll element. However, in certain scroll-type hermetic compressors, particularly those whose motor is arranged in the discharge pressure portion of the hermetic envelope, there is a resultant axial thrust load exerted on the drive shaft which extends between the motor and the volute orbital element. This load results from the fact that the drive shaft usually has an end disposed in the discharge pressure portion, which end has a plane subjected to the discharge pressure, and a second end disposed in the suction pressure portion. this end having a plane subjected to the suction pressure. Since the suction pressure is lower than the discharge pressure, the shaft is subjected to a resulting thrust force directed towards the suction pressure portion of the hermetic envelope. Currently, the drive shaft is equipped with a thrust bearing preventing the shaft from moving in an axial direction. This is undesirable because energy is dissipated in the thrust bearing, which energy could otherwise be used to operate the volute orbital element. This reduces the efficiency of the compressor and requires a larger engine than would otherwise be required if the thrust was not present. In addition, the thrust bearing is often relatively more expensive and subject to greater wear, thereby reducing the service life of the bearing.

compressor and increases the maintenance requirements.

The object of the invention is therefore to increase the efficiency of a compressor by eliminating the need for a

thrust bearing on the drive shaft.

Another object of the invention is to reduce the cost of operation and manufacture of such a device.

compressor assembly.

Another object of the invention is to achieve the above objects while increasing the useful life and reducing the maintenance requirements of this compressor.

The invention thus relates to a drive shaft

for a compressor, advantageously of the scroll type. The invention includes a drive shaft having an end having a plane disposed in a portion at the discharge pressure of a hermetic envelope and a second end disposed in the portion at the suction pressure of the hermetic envelope. The second end has a cavity defined by a circular side wall and a recessed surface. The cavity cooperates with the drive hub of the orbital scroll element to define a closed chamber containing a fluid

under pressure subjected to the discharge pressure.

The planar extent of the recessed area within the chamber and the planar extent of the end of the shaft in the discharge pressure portion are proportionally dimensioned to exert a resultant axial thrust such as than desired on the drive shaft. Therefore, the resulting axial thrust on the drive shaft can be selected by preparing a drive shaft having the plan extent of the desired surface exposed to the delivery pressure, which allows the use of bearings that can withstand only radial load and eliminates the need for a thrust bearing

for the drive shaft.

The invention will be described in more detail with reference to the accompanying drawings by way of non-limiting example and in which: - Figure 1 is an axial section of a hermetic compressor comprising a drive shaft according to the invention; and

FIG. 2 is a diagrammatic representation

than a refrigeration system with a compressor

hermetic according to the invention.

A compressor system, designated globally by

20, is shown in FIG.

The compressor system 20 is a rotary compressor, housed in a hermetic envelope 22. The hermetic envelope is advantageously of generally cylindrical shape,

consisting of an upper part 24, an inner part

26 and a central portion 28. The central portion 28 includes a peripheral heat exchange portion composed of a plurality of spaced parallel annular ribs 30 for effecting heat exchange.

from the inside of the hermetic envelope 22 to the environ-

outside. The central portion 28 of the hermetic envelope 22 includes a frame portion 32 for dividing the hermetic envelope 22 into a portion 34 at the discharge pressure and a portion 36 at the suction pressure. The central portion 28 is advantageously fixed by welding to the upper portion 24 and the lower portion 26, by their respective peripheral edge, so that the casing 22 is suitably divided to form the parts at the discharge and suction pressures. A motor 40 is disposed in the portion 34 at the discharge pressure of the hermetic envelope 22. The motor 40 is advantageously an electric motor having a fixed stator 42 and a rotating rotor 44 separated by an annular space. The motor is not described in detail since the technique of electric motors is generally well known. However, the motor 40 is in general and preferably an electric motor operating on single-phase or three-phase alternating current. It is also possible to operate the compressor assembly 1 in the manner of a speed device

variable by setting up an electric motor con-

Viable 40 or a suitable regulator (not shown)

to vary the speed of the motor 40.

The compressor assembly 20 of the preferred embodiment is advantageously a scroll-type compressor having a fixed scroll winding 50 and an orbital scroll winding 52. The fixed scroll winding 50 is attached to, or is part of, the lower portion 26 of the hermetic envelope so that a portion of this lower portion 26 has a substantially planar surface acting in the manner of an end plate to establish a sealed orbital contact with the orbital scroll coil 52. The volute winding

orbital 52 is attached to, or forms part of, a license plate.

tremity 54 with orbital movement.

The fixed scroll winding 50 and the orbital scroll winding 52 are involute-shaped, each having a tip 56 for sealing against the opposite end plate, and sidewall surfaces 58 for linear contact, each with the

flank surface 58 of the adjacent volute winding.

The end plate 54 with orbital scroll also comprises a circular drive means 66 disposed on the opposite side to that of the volute winding

orbital 52. The drive means 70 advantageously

molding die with the end plate 54 and is located approximately in the center of this plate 54. An opening 72 forming a discharge orifice is defined

through the end plate 54 and the drive hub

70 by a bore adjacent to the radial end

of the orbital scroll winding 52. The opening

The discharge head 72 allows a fluid to exit the scroll coils 50 and 52 when compressed into

these latter.

The compressor assembly 20 further includes an Oldham coupling 80 or similar anti-rotation device for preventing the orbital end plate 54 from rotating while allowing it to perform a rotation.

Orbital motion around an axis. Anti-devices

rotation such as mating Oldham 80 are generally well known in the art and will not be

described here because a detailed description of such

devices does not seem essential to understanding

of the invention.

A thrust bearing 84 is disposed between the central frame portion 32 and the orbital volute end plate 54 to provide an appropriate axial contact of the respective ends 56 of the scrolls with the opposite end plates. It is also possible to make the ends 56 of the volutes contact by applying a fluid to the discharge pressure or to the intermediate pressure between the discharge and suction pressures at a pressure of 50.degree.

selected portion of the orbital volute end plate.

The thrust bearing 84 and the use of fluid pressure therefor are well known to those skilled in the art and will not be further described herein for this reason. One can see, for example, the patent of the United States of America

No. 4,715,733.

A drive shaft 100 is disposed within the sealed housing 22. The drive shaft 100 passes through an opening 102 in the central frame portion 22. This opening 102 of the frame is located substantially centrally so that the drive shaft 100 communicates from the portion 34 to pressure of

discharge to the portion 36 at suction pressure.

The opening 102 of the frame also comprises an upper radial bearing 104 and a lower radial bearing 106 arranged between the drive shaft 100 and the opening 102 of the

constructed to allow the shaft 100 to rotate.

Bearing 104 may be a plain bearing or bearing formed, for example, of sintered bronze, or may be a roller bearing (as shown for bearing 106) or a ball bearing. In all cases, the bearing 104 must substantially seal between the drive shaft 100 and the opening 102 of the frame to prevent fluid leakage from the portion 34 to pressure of

discharge to the part 36 at the suction pressure.

A separate sealing element (not shown) could also be used for this purpose. It should be noted that a minimum amount of leakage fluid may be desirable in some cases to promote the flow of oil through the bearings 104 and 106. The drive shaft 100 has a first end 108 disposed in the discharge pressure portion 34 and a second end comprising a crank 110 disposed in the suction pressure portion 36. The crank has a circular outer surface 112 for making rotational contact with the lower radial bearing 106 and a relatively eccentric circular inner sidewall 114 surrounding a recessed flat surface 116 which defines a crank cavity for engaging with the crank cavity. A bearing 118 is advantageously disposed between the circular side wall 114 and the drive hub 70 to allow transmission of a rotational movement of the drive shaft 100 to the drive hub 70. The bearing 118 makes a tight contact to define a closed chamber between the drive hub 70, the flat surface

recessed 116 and the circular side wall 114.

A discharge gallery 120 extends axially through the drive shaft 100, establishing a flow communication between the load defined in the crank portion 110 of the drive shaft 100 and the pressure portion 34. of repression. In its simplest form, the discharge gallery 120 is simply an axial bore connecting the plane recess 116 at the end.

opposite of the drive shaft 100.

The central portion 32 of the frame advantageously has a recess for containing a lubricant reserve 130. This lubricant is advantageously an oil of a type commonly used in the refrigeration system. A lubricant metering opening 140 is provided in the lower portion of the lubricant reservoir 130. This lubricant metering opening 140 is of a relatively small bore, sized to provide a continuous and convenient lubricant flow from the reservoir 130 of the lubricant to the pressure part 36

suction of the hermetic envelope 22.

A bore defining a lubricant passage 150 from lubricant reservoir 130 to the upper radial bearing 104 is also defined in FIG.

32 center casting part.

For the operation of the compres-

however, the motor 40 is turned on so that the rotor 44 rotates. The rotor 44 is connected to the drive shaft 100 so that the latter transmits this rotation by means such as a forced fit or a mounting to

key and corresponding grooves (not shown).

The drive shaft 100 rotates in the housing opening 102 on the bearings 104 and 106, while communicating a rotation to the drive hub 70 through the bearing 118 in the crank cavity defined by the side wall. 114. The orbital scroll end plate 54 attached to the drive hub 70 is constrained by the Oldham coupling 80 to orbital motion relative to the fixed scroll winding 50, causing several chambers to form between the flanks 58 of the relative scroll windings. The volume of the chambers thus formed decreases towards the inner radial end of the windings 50 and 52 so that a fluid is sucked inwards from the chambers forming at the inner radial ends of the windings 50 and 52, compressed during the orbital movement of the chambers towards the radially inner ends of the windings 50 and

52 and discharged through the discharge opening 72.

The discharged fluid enters the chamber closed by the drive hub 70, the recessed flat surface 116 and the circular side wall 114. The fluid passes from this chamber into the discharge pressure portion 34 through the discharge gallery 120 arranged in the tree

100 training.

In operation, when the refrigerant

rant or other fluid is compressed as mentioned above.

above, the fluid at the discharge pressure causes a small forced flow of lubricant through the lubricant metering opening 140 and the lubricant passage 150. The lubricant entering part 36 at the suction pressure lubricates Oldham's coupling mechanism, and any abutments applied to the end plate 54 of the orbital winding and at the end 56 and to the surfaces of the sidewalls 58 respective scroll windings. Lubricant entrained in the lubricant passage lubricates the upper radial bearing 104 and flows from the bearing 104 to the lower radial bearing

106 then in part 36 at the suction pressure.

The lubricating oil is driven by the refrigerant fluid or other compressed fluid and forced into the discharge opening 72 and the discharge gallery 120

to enter Part 34 at the pressure of

where it is no longer driven by the coolant or other compressed fluid, as the case may be, and descends by flowing in the annular space between the stator 42 and 44 into the reservoir 130 of lubricant, or between the elements 42 and 28 by taking other passages (not shown).

An examination of Figure 1 and the description

above shows that only the surfaces of the planar areas delimited by the S and F diameters

produce an axial thrust on the drive shaft 100

This is because all the pressure forces acting in any direction normal to the axis of the drive shaft 100 are canceled by an opposite opposing force. The surface of the plane spread is the surface considered parallel to the axis of the drive shaft 100. Therefore, it can be seen that the resulting thrust load on the drive shaft 100 is determined by the delivery pressure acting on the planar recess 116 and on the end of the drive shaft 100 disposed in the part 34 at the discharge pressure. The crank portion 110 is subjected to fluid suction pressure on all sides with the exception of the planar recess 116 and thus exerts only a large resultant push load on the drive shaft. The axial thrust load is therefore determined by the area of the planar extent determined by the diameter F of the drive shaft 100, as opposed to the area of the extension.

plane determined by the diameter S of the planar recess 116.

For example, the values of S and F may be chosen to be equal to establish a pressure equilibrium generating zero resultant axial thrust on the drive shaft 100, or the value of the diameter S may be chosen so that to be larger than that of the diameter F so that the drive shaft 100 acts to support the weight of the rotor 44 to which it is connected. The compressor unit 20 can advantageously be used in an air conditioning or refrigeration system comprising a condenser 200 intended to condense the refrigerant fluid to make it liquid, an expander 200 intended to receive the cooling fluid in the liquid state coming from the condenser 200 and to relax this refrigerant, an evaporator 230 for receiving the refrigerant expanded from the expander 220 and evaporating the refrigerant, a suction pipe 240 for transmitting the evaporated refrigerant to a suction port 242 located in the lower portion 26 of the hermetic envelope 22 so that the coolant is received in the portion 36 at the suction pressure. Then the refrigerant is compressed as described above and discharged from the compressor assembly 20 through a discharge orifice 244

then by a pipe 246 of repression until the conden-

200. A schematic representation of such a system

air conditioning is shown in Figure 2.

In such an air conditioning air conditioning system, the compressor assembly 20 can have a capacity ranging, for example, from 4.5 to 13.5 tons. The pressure of the refrigerating fluid prevailing at the suction orifice 242 is usually between 0 and 700 kPa, while the delivery pressure of the refrigerant, produced by the compressor assembly 20 at the outlet orifice 244, is usually between 1400 and 2800 kPa. The combined weight of the rotor 44 and the drive shaft 100 is currently between 2.25 and 16 kg. The diameter S may be, for example, equal to 125% of the diameter F so that the resulting axial thrust load of the drive shaft 100 supports the rotor 40 and the drive shaft 100 during the normal operation of the drive. compressor assembly 20, thus eliminating the need for a thrust bearing to support the drive shaft 100. The weight of the rotor 44 and the drive shaft 100 is transmitted to the volute end plate 54 orbital via the gas at the discharge pressure in the chamber. This has the additional advantage of increasing the axial flexibility and therefore the

yield of volutes 50 and 52.

It is obvious to one skilled in the art that such a refrigeration system could comprise several compressor assemblies 20 and several other components, as well as other improvements such as hot gas defrosting, all of which are well known in the art. the skilled person. The compressor assembly 20 comprising the drive shaft 100 axially balanced in pressure, is a simplified compressor construction and less expensive, whose maintenance and energy requirements are reduced, eliminating the need for a thrust bearing which is inefficient and reduces power. It also appears that the axially balanced pressure drive shaft 100 offers greater latitude in the compressor design in that the drive shaft chamber can be varied by the appropriate choice of diameters. S and F to get

the opposite and desired surfaces of the planes.

It goes without saying that many modifications can be made to the compressor described and shown

without departing from the scope of the invention.

Claims (21)

1. fluid compressor, characterized in that it comprises a hermetic envelope (22) comprising a frame (32) which divides it into a part (36) at a suction pressure and a part (34) at a pressure of outlet and which further has a generally central bore (102), a first scroll element (52) mounted

to be able to turn in the suction pressure part

the sealed envelope having an end plate (54) having a first upwardly involute portion and a drive hub (70) which further has a bore defining a discharge aperture (72), a second scroll member (50) projecting outwardly in the suction pressure portion of the airtight envelope, the second involute scroll member being interwoven with the first involute scroll member, a motor (40). disposed in the discharge pressure portion of the hermetic enclosure, and an axially-balanced pressure-driven drive shaft (100) rotatably mounted in the hermetic enclosure and drivingly engaged with the motor, the shaft having a first end (108) disposed in the central bore of the frame connecting the suction and discharge pressure portions of the hermetic shell, the first end being substantially sealingly mounted in the central bore, and a second portion (110) located in the suction pressure portion of the hermetic envelope for establishing a grip, under a restoring force, with the hub

driving the second scroll element.

2. fluid compressor according to claim 1, characterized in that the drive shaft has an axial bore (120) for transmitting a refrigerant involute volutes interleaved to said

part to the discharge pressure.

Fluid compressor according to claim 2, characterized in that the second portion of the drive shaft further defines a circular cavity (116).

intended to house in rotation the drive hub.

4. fluid compressor according to claim 3, characterized in that the circular cavity of the second portion of the drive shaft is further defined by an eccentric bore relative to the axial bore of

the drive shaft.

5. Compressor fluid according to the claim

4, characterized in that the second portion of the drive shaft further comprises means (106) for supporting a rotational movement between the second portion of the drive shaft and the hub. of training so that the latter and the tree cooperate

to form a room.

6. Fluid compressor according to the claim

5, characterized in that the circular bore defined in the second portion of the drive shaft has a first diameter (S) and the first end has a

outer diameter (F).

Fluid compressor according to Claim 6, characterized in that the drive shaft and the drive hub define a closed chamber containing a fluid at the discharge pressure which acts on a pressure medium.

surface delimited by the diameter (S).

A fluid compressor according to claim 7, characterized in that the support means further comprises a seal between the closed chamber defined by the drive hub and the drive shaft and the portion

at the suction pressure.

9. fluid compressor according to claim 8, characterized in that the drive shaft is axially balanced in pressure by a fluid at the discharge pressure acting on a surface defined by the diameter (S) and by a fluid at the discharge pressure acting on a surface delimited by the

diameter (F).

10. Compressor fluid according to the claim

9, characterized in that the frame furthermore has

function of supporting the motor inside the

hermetic veloppe.

11. Compressor fluid according to the claim

10, characterized in that the frame further comprises a

lubricant reservoir (130).

12. Compressor fluid according to the claim

11, characterized in that the frame further has a lubricant metering opening (140) providing metering flow communication for a lubricant between the lubricant reservoir and the suction pressure portion therein. of which the lubricant is

driven with the fluid.

13. Compressor fluid according to the claim

12, characterized in that the motor comprises a stator (42) and a rotor (44) defining an annular space in which the lubricant is no longer driven by the fluid and

flows to the tank.

14. Compressor fluid according to the claim

11, characterized in that the frame further comprises means (104) for supporting a rotational movement

of the tree.

15. Compressor fluid according to the claim

14, characterized in that the support means further comprises a seal between the pressure portion of

discharge and the part at the suction pressure.

16. Compressor fluid according to the claim

15, characterized in that the frame furthermore has a

passageway (150) with lubricant from the lubricant reservoir

trusting to the support.

17. Fluid compressor according to the claim

9, characterized in that the diameter (S) is relative-

larger than the diameter (F) to support the weight

of the drive shaft and a portion of the motor weight.

18. Refrigeration system for circulating a refrigerant in a closed loop, characterized in that it comprises a condenser (200) for condensing the refrigerant to make it pass in the liquid state, a pressure reducer (220) for receiving liquid refrigerant from and condensing the condenser, an evaporator (230) for receiving the expanded coolant from the expander and for evaporating it, and a compressor (20) for receiving the evaporated refrigerant from of the evaporator and compressing it, said compressor comprising a hermetic envelope (22) having a frame (32) which divides it into a portion (36) at a suction pressure and a portion (34) at a discharge pressure and which further has a generally central bore (102), a first volumetrically mounted element (52)

turn in the suction part of the

hermetic veloppe and having an end plate

(54) of which is a first part developing

and a drive hub (70), the latter presents

in addition a bore defining a discharge aperture (72), a second involute volute member (50) projecting into the suction pressure portion of the hermetic envelope, the second involute volute member being interwoven with the first involute volute element, a motor (40) disposed in the discharge pressure portion of the hermetic envelope, and an axially balanced pressure drive shaft (100) rotatably mounted in the housing; hermetically sealed casing having a first end (108) in the central bore of the casing interconnecting the suction pressure and discharge pressure portions of the hermetic casing, the first end having an outside diameter (F), and a second crank portion (110) located in the suction pressure portion of the hermetic envelope, the second crank portion having a circumferential cavity 116 (S) of diameter (S) for establishing a grip, under a restoring force, with the drive hub of the second scroll element.

19. Refrigeration system according to the

18, characterized in that the drive shaft is axially balanced in pressure by a fluid at the discharge pressure acting on a surface delimited by the diameter (S) and by a fluid at the discharge pressure acting on a surface bounded by the

diameter (F).

20. Process for axial balancing in pressure of a drive shaft in a hermetic fluid compressor, characterized in that it consists in using a frame (32) dividing the hermetic envelope (22) into a part (36). ) at a suction pressure and a portion (34) at a discharge pressure, the frame further having a generally central bore (102), having a first rotatably mounted scroll member (52), in the suction pressure portion of the airtight envelope, the first scroll member having an end plate (54) having a first protruding portion and a drive hub (70),

the volute element further having a defined bore

a discharge opening (72), to have a second involute volute projecting in the suction pressure portion of the hermetic envelope, the second involute volute being nested with the first involute volute, a motor (40) being arranged in the discharge pressure portion of

the hermetic envelope, to use a shaft (100) of

with a first end (108) housed in the central bore of the frame connecting the portions to the suction pressure and the discharge pressure of the hermetic envelope, the first end having an outer diameter (F) and a second crank portion (110) located in the suction pressure portion of the hermetic envelope, the second crank portion having an eccentric circular cavity (116) of diameter (S) for setting a grip, under a force of recall, with the drive hub of the second element to

volute, and to apply a fluid to the pressure of

on a surface delimited by the diameter (S) and on

a surface delimited by the diameter (F).

21. A method for axially balancing a drive shaft in a hermetic fluid compressor, characterized in that it consists in producing the drive shaft (100) so that a first end (108) has a outer diameter (F) and that a second portion (110) has an eccentric circular cavity (116) of diameter (S), to select the outer diameter (F) and the diameter (S) of the circular cavity to produce on the drive shaft a desired axial resultant thrust of balancing, and applying a fluid to the discharge pressure on a surface delimited by the diameter (S) and, oppositely,

Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump, or combined organic rankine and heat pump cycle